EP0220094B1 - Federungsaggregat mit Schwingenarm für Fahrzeuge - Google Patents

Federungsaggregat mit Schwingenarm für Fahrzeuge Download PDF

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Publication number
EP0220094B1
EP0220094B1 EP86402036A EP86402036A EP0220094B1 EP 0220094 B1 EP0220094 B1 EP 0220094B1 EP 86402036 A EP86402036 A EP 86402036A EP 86402036 A EP86402036 A EP 86402036A EP 0220094 B1 EP0220094 B1 EP 0220094B1
Authority
EP
European Patent Office
Prior art keywords
piston
axis
slide member
arm
longitudinal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP86402036A
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English (en)
French (fr)
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EP0220094A1 (de
Inventor
Jean-Marc Chauveau
Claude André Chambon
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LUCAS FRANCE SA
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LUCAS FRANCE SA
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Publication of EP0220094A1 publication Critical patent/EP0220094A1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/104—Suspension devices for wheels, rollers, bogies or frames
    • B62D55/112—Suspension devices for wheels, rollers, bogies or frames with fluid springs, e.g. hydraulic pneumatic
    • B62D55/1125—Hydro-pneumatic or pneumatic, e.g. air-cushioned
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/10—Connection to driving members

Definitions

  • the present invention relates to a swinging arm suspension member for vehicles.
  • the connecting means of the connecting rod with the piston consist of a direct articulation of this connecting rod on the piston, around the fourth axis.
  • the movements of the suspension necessarily entail an obliquity of the connecting rod relative to the longitudinal direction of the cylinder, in certain angular positions of the arm relative to to the support, and this obliquity results in the application to the piston, by the connecting rod, of forces themselves oblique with respect to the longitudinal direction of the cylinder; the longitudinal component of these forces results in a longitudinal displacement of the piston relative to the cylinder, in a desired manner, while the transverse component of these forces results in increased friction between the piston and the cylinder, which counteracts the longitudinal movement piston; moreover, if it is taken into account that the transverse forces undergone by the piston are transmitted to the cylinder via the seals, the pivoting movement of the connecting rod relative to the piston, around the fourth axis, results in variable compressions of the seals between the piston and the cylinder, which can lead to premature deterioration of the seals and the appearance of leaks between the piston and the cylinder.
  • the structure recommended according to the invention does not mean that the drawbacks appearing at the level of the piston and of the seals between the latter and the cylinder are simply transferred to the slide in a traditional structure, in the measure where one can be satisfied with ensuring contact between the slide and the cylinder just enough to provide guidance for relative longitudinal sliding, without it being necessary on the other hand to provide sealing at this level; on the contrary, according to a preferred embodiment of the present invention, means such as channels passing through the slide longitudinally right through are provided for introducing a lubricant between the slide and the piston, to perfectly lubricate one and the other and their means of mutual connection; these advantageously consist of mutual abutment means in the direction of a relative longitudinal approximation, the action of the compressible fluid forming a spring resulting in permanent contact of these mutual abutment means; thus, the transverse components of force to which the slide can be subjected does not trans put only negligibly on the piston.
  • the cylinder is defined, inside the arm, by a longitudinal jacket attached to the latter, which also makes it possible to reduce the deformations of the cylinder resulting from the flexing of the arm, as well as the consequences of such deformations.
  • This member designated by the general reference 1, is illustrated in equilibrium positions that it is likely to occupy while it is mounted on a vehicle which has been shown schematically in 2 a frame, and that this vehicle rests on a horizontal plane by means of a rolling member shown diagrammatically at 3, such as a wheel or a track roller, depending on the type of vehicle considered.
  • the suspension member 1 which has been illustrated comprises a support 4 in the form of a vertical plate 6 which can be secured, for example by bolting 5, with the frame of the vehicle and which itself carries in solidarity, for example in one piece with it, a shaft 7 having an average direction 8 horizontal, perpendicular to the plate 4; when the support 4 is secured to the frame 2 of the vehicle, the shaft 7 protrudes outside of it.
  • the shaft 7 itself carries in solidarity, in particular against a rotation about an axis defined by its mean direction 8, a crank 9 which cooperates for this purpose with the shaft 7 by complementarity of shapes ; for example, the crank 9 has a bore 10 by which it fits on the shaft 7 and, transversely with respect to the axis 8, the bore 10 and the shaft 7 have respective polygonal, complementary sections, as shown in Figure 2; any other form of mutual securing of the crank 9 and of the shaft 7 in particular against a relative rotation about the axis. 8 could be used without departing from the scope of the present invention; for example, one could use for this purpose a traditional keying, or a cooperation of the bore 10 and the shaft 7 by complementary grooves.
  • the crank 9 forms on the one hand, above the shaft 7, a yoke 11 integrally carrying a pin 12 with an axis 13 located parallel to the axis 8, above the latter and in a same vertical plane 14 as this; this axis 13 is like the axis 8 fixed relative to the support 4; on the other hand, respectively on either side of the yoke 11 in a direction parallel to the axis 8, the crank 9 integrally defines two sleeves 20 and 21 located respectively between the yoke 11 and the plate 6, and opposite the plate 6 relative to the yoke 11; each of the sleeves 20 and 21 integrally carries the inner cage of a respective thrust bearing 16, 17 furthermore having an outer cage secured respectively to a housing 18 or a housing flange 19, one and the other annular and mutually integral, for guiding the housing 18 and the housing flange 19 in rotation about the axis 8 relative to the crank 9 and the shaft 7 without possibility of relative translation parallel to axis 8; for this purpose, in addition, the inner cages of the bearings 16 and 17 are
  • the housing 18 is sealed and envelops the crank 9 on the side of the plate 6 of the support 4 and in the direction of a radial distance with respect to the axis 8; around the bearing 16 and the sleeve 20, the casing 18 projects projecting towards the plate 6 an annular ring 23 of revolution around the axis 8, which ring 23 is engaged, with the possibility of relative rotation about the axis 8, in a complementary groove 24 arranged in the plate 6; seals 25, 26 the choice and position of which are easily determinable by a person skilled in the art provide a seal between the plate 6, which is itself sealed, and the crown 23 which is also sealed.
  • the flange 19, also leaktight, is tightly secured to the housing 18 and covers the crank 9 opposite the housing 18; it has an orifice of revolution around the axis 8, closed in leaktight manner by an attached cover 27, in the general shape of a disc perpendicular to the axis 8; similarly, an orifice in the housing 18 is sealed off by an attached cover 28, so that the support 4, the housing housing 18, the housing flange 19, the cover 27, the cover 28 together define a sealed housing 22 enclosing in particular the crank 9, the pin 12 and the two bearings 16 and 17.
  • the casing 22 contains a substantially incompressible hydraulic fluid sible, in practice an oil, which fills to the maximum this casing 22 which may also contain air.
  • the housing 18 integrally carries, preferably in one piece, a hollow longitudinal arm 29, projecting from the casing 22, along a mean plane 30 perpendicular to the axis 8 and coincident with the section plane identified in I-l in Figure 3.
  • the arm 29 is illustrated in a horizontal orientation in FIG. 2, but it is understood that it can rotate jointly with the casing 22, of which it is integral, around the axis 8 relative to the support 4; this arm 29 has a downward obliquity, starting from the casing 22, in its state illustrated in FIGS. 1 and 4.
  • the arm 29 Longitudinally opposite its connection with the housing 18 of the casing 22, the arm 29 carries integrally, advantageously in one piece, a rocket 36 for guiding the rotation relative to it, about an axis 37 parallel to axis 8, of the rolling member 3; in the state illustrated in FIG. 2, a plane 38 common to axes 8 and 37 is horizontal but it can also be oblique, since variations in the relative level of the framework 2 of the vehicle and of the rolling member 3 result in a rotation of the arm 29 around the axis 8 relative to the support 2.
  • the arm 29 is hollowed out of two tubular cavities 31 and 32 having respective longitudinal axes 33, 34 rectilinear, parallel with respect to each other as well as with respect to the plane 38 and situated in the plane 30 so that the cavity 31 is placed above the cavity 32, that the axes 33 and 34 are both located above the plane 38, and that the axis 33 of the upper cavity 31 intersects the plane 14 in the immediate vicinity of the axis 13, in the nonlimiting example illustrated.
  • the cavities 31 and 32 communicate freely with the interior of the casing 22 while at their other transverse end, constituting the zone of the arm 29 furthest from the casing 22, they are closed by a leaktight cover 35, attached in an integral and leaktight manner to the arm 29 itself leaktight.
  • the lower cavity 32 is closed off permanently by a sealed partition 40, attached integrally to the arm 29, so that the lower cavity 32 has on the one hand, close immediately of the housing 18, a chamber 41 in direct communication with the interior of the casing 22, and on the other hand, in the immediate vicinity of the cover 35, a chamber 42 which communicates itself permanently, via a hole 39 for passage fluid arranged between the two cavities 31 and 32 in a direction 43 perpendicular to the two axes 33 and 34, with the cavity 31.
  • a sealed partition 40 attached integrally to the arm 29, so that the lower cavity 32 has on the one hand, close immediately of the housing 18, a chamber 41 in direct communication with the interior of the casing 22, and on the other hand, in the immediate vicinity of the cover 35, a chamber 42 which communicates itself permanently, via a hole 39 for passage fluid arranged between the two cavities 31 and 32 in a direction 43 perpendicular to the two axes 33 and 34, with the cavity 31.
  • the latter is internally lined with a longitudinal tubular jacket 44, of axis 33, which is pierced with one or more orifices 46 opposite the hole 39 and a groove 45, annular of revolution around the axis 33, through which the hole 39 opens into the cavity 31 near the cover 35.
  • the jacket 44 serves to facilitate the guiding of the longitudinal sliding, inside the tubular cavity 31, of a sealed piston 47, sealed with respect to the jacket 44 by suitable fittings 48, which piston 47 is connected by a connecting rod 49 to the pin 12 carried integrally by the crank 9, so that the angular deflections of the arm 29 around the axis 8 relative to the support 9 result in a longitudinal sliding movement of the piston 47, in one way or the other, inside the cavity 31.
  • the connecting rod 49 has a first end 50 by which it is articulated on the pin 12, preferably by means of a ball joint device 51, so as to be able to pivot around the axis 13 relative to the crank 9; the connecting rod 49 also has a second end 51 disposed inside the cavity 31, and which itself has the shape of a spherical ball joint 52 whose center 53 is held on the axis 33 by engagement of the ball joint 52 in a concentric spherical bearing 54 of an annular slide 55, of revolution around the axis 33, which slide 55 is mounted for longitudinal sliding in the jacket 44, on the same side of the piston 47 as the axis 13.
  • the slider 55 is in turn designed to allow the hydraulic fluid contained in the casing to pass freely 22 and in the chamber 57 towards a space 58 remaining between this slide 55 and the piston 47; for this purpose, for example, longitudinal passages 59 are drilled in the slide 55, around the spherical bearing 54; thus, the fluid contained in the casing 22 and the chamber 57 can reach the space 58 and lubricate the slide 55 and the piston 47 in contact with the jacket 44, the ball joint 52 in contact with the spherical bearing 54, thus that in contact with a pad 60 attached integrally to the piston 47, on the side of the chamber 57, to serve as a means of longitudinal abut
  • the piston 47 is biased longitudinally towards the slide 55, so as to ensure mutual abutment of the buffer 60 and of the ball joint 52 in the example illus very, by a compressible fluid forming a pneumatic spring, in practice a gas, housed in the communicating chambers 56 and 42 and acting directly on the piston 47 in the chamber 56; the hole 39, the groove 45 and the orifice 46 (or the orifices 46) are dimensioned so as to prevent practically no obstacle to the passage of this fluid from one to the other of the chambers 56 and 42, c that is to say so as not to cause any rolling of this fluid when the piston 47 slides longitudinally inside the jacket 44.
  • a compressible fluid forming a pneumatic spring, in practice a gas, housed in the communicating chambers 56 and 42 and acting directly on the piston 47 in the chamber 56; the hole 39, the groove 45 and the orifice 46 (or the orifices 46) are dimensioned so as to prevent practically no obstacle to the passage of this fluid from one to the other of the chambers 56 and
  • the compressible fluid forming a spring bathes a bladder 61 of flexible, leaktight, elastically extensible material, which bladder 61 has, towards the partition 40, along the axis 34, an orifice 62 advantageously delimited by a nozzle 67 forming an integral part from the bladder 61 and placed projecting along the axis 34 towards the partition 40; by its radially outer periphery 63, with reference to the axis 34, the end piece 67 engages in a bore 66, of axis 34, arranged in a sealed wall 64 attached integrally and tightly in the cavity 32, transversely to the axis 34, so as to double the partition 40 towards the chamber 42 by delimiting with the partition 40, in the cavity 32, an intermediate volume 65 sealed as well with respect to the chamber 41 as with the rest of the room 42; the entire outer periphery 63 of the end piece 67 is in sealed contact with the wall 64, which defines through it a passage 68 connecting the interior of the bladder 61 with the volume
  • the bladder 61 thus delimits internally, inside the chamber 42, a chamber 69 which is intended to receive, via the volume 65, a substantially incompressible hydraulic fluid whose role is to reduce the volume available, to the inside the chamber 42, for the compressible fluid forming a spring and, by a variation in the volume of the chamber 69 following an introduction or removal of a substantially non-compressible hydraulic fluid in this chamber, to force a more or less quantity compressible fluid to remain in the chamber 56 to vary the longitudinal position of the piston 47 in the jacket 44 corresponding to the balance between the weight of the vehicle and the support of the rolling member on the ground, that is to say -to say, in other words, to vary the ground clearance.
  • conduits shown diagrammatically by a dashed line 70 are arranged inside the arm 29, the housing flange 19 and the cover 27, in a manner easily determinable by a person skilled in the art, for connecting on the one hand the volume 65 intermediate between the partition 40 and the wall 64, and on the other hand a chamber 71 arranged in the cover 67, along the axis 8 as shown in Figure 3; the chamber 71, placed opposite the shaft 7 along the axis 8, accommodates in a manner integral with the cover 27, with mutual sealing, one end of a tube 72 of axis 8, which tube 72 passes through the shaft 7 up to the plate 6, along the axis 8, by a bore 73 arranged in the shaft 7 with dimensions such that there remains a peripheral clearance between the tube 72 and the shaft 7; at the level of the plate 6, the tube 72 is guided in rotation relative to the support 4, around the axis 8, by a bearing 74 provided with a rotary seal 75, and is connected to a sealed chamber 76 fitted in the plate 6 and connected itself, by a bearing
  • the bladder 61 could be omitted and replaced by a piston 79, shown diagrammatically in phantom in Figure 2, which would be slidably mounted in the chamber 42 to subdivide it- ci in a sealed manner, between a part of the chamber in direct communication with the chamber 56 through the hole 39, and into a part of the chamber, corresponding to the chamber 69, in fluid connection with the volume 65 by the bore 66 of the wall 64.
  • the chambers 56 and 42 connected by the hole 39 in the example illustrated could be placed in respective alignments that are not parallel to each other. and / or relative to plane 38, along plane 30 or offset from it; one could in particular have the chambers 56 and 42 in the same longitudinal alignment, for example defined by the axis 33, in which case the piston 47 would succeed one another, the chambers 56 and 42 combined, the bladder 61 or the piston 79 , the chamber 69 and the wall 64 which could then be defined by a cover replacing the cover 35; such a variant has not been illustrated, but its realization from the mode of implementation illustrated and described above is in the domain of normal skills for those skilled in the art.
  • the device which has just been described constitutes an air spring with the possibility of adjusting ground clearance, and can be used as such on a vehicle.
  • damping means are here constituted by the braking means acting, with a braking force controlled by the speed of rotation of the arm 29 relative to the support 4, between members secured respectively to the arm 29 and to the support 4, at l against a relative rotation around axis 8.
  • the crank 9 carries downwards, that is to say opposite to the yoke 11, a plurality of dovetail ribs 80 parallel to the axis 8 and receiving, with the possibility of relative sliding parallel to this axis, but without the possibility of relative rotation around this axis, grooves of complementary shape 81 arranged in sectors 82 of brake discs, which sectors 82 are juxtaposed along axis 8 perpendicularly to which they have respective mean planes; the brake disc sectors 82 are two in number in the example illustrated, but only one of these sectors could be provided as well as one could provide more than two.
  • the brake disc sectors 82 are arranged inside the casing 22, between the casing housing 18 and the casing flange 19.
  • the housing 22 carries in solidarity, by means of the cover 28 located in the dihedral defined by the planes 38 and 14, under the plane 38 and on the same side of the plane 14 as the arm 29, a plurality of blades 83 having respective mean planes perpendicular to the axis 8, the number and arrangement of these blades 83 being such that each disc sector 82 is interposed between two of these blades; in other words, in the example illustrated, three of these blades 83 are thus provided, one of which is interposed between the two disk sectors 82 while the other two are placed respectively on either side of the assembly thus formed by the two disk sectors 82 and by the intermediate blade 83.
  • Each of the extreme blades 83 carries a brake lining 84 of known type, towards the immediately adjacent disc, while the blade 83 intermediate between two sectors of discs 82, or each blade of this type, carries on both sides a lining of braking 84.
  • the blades 83 cooperate by conjugation of shape with grooves 127, 128 parallel to the axis 8 and defined jointly by the cover 28 and the housing 18; these grooves 127,128 guide the blades 83 to slide in a direction parallel to the axis 8; while that of these blades 83 which is closest to the plate 6 of the support 4 bears against the housing 18 parallel to the axis 8, that of these blades 83 which is the farthest from the support 4 is that is to say the one closest to the flange 19, is biased by a hydraulic thrust cylinder 85, capable of applying to this blade 83 and, by means of the latter, to all of the disk sectors 82 via the linings
  • the flange 19 has towards the support 4, that is to say towards the inside of the casing 22, at least one blind hole 86 of axis 87 parallel to the axis 8, opposite the plate 83 closest to the flange 19, and this blind hole constitutes a cylinder in which can move, along the axis 87, a piston 88 sealed vis-à-vis the blind hole 86 by a seal 89 to delimit the 'Inside the blind hole 86 a sealed chamber 90; in this chamber 90, is advantageously housed a helical compression spring 91 shown diagrammatically by dashed lines, which spring 91 ensures a minimum contact pressure between the brake linings 84 and the disc sectors 82 even in the absence of any fluid under pressure inside chamber 90.
  • this chamber 90 also encloses such a fluid, the pressure of which is varied as a function of the speed of rotation of the arm 29 relative to the support 4 around the axis 8, as a function of predetermined evolution laws, some examples of which , not limiting, will be described later.
  • the shaft 7 carries integrally, for example by bolting 92, inside the housing 22 and directly facing the cover 27, a cam having a mean plane 100 perpendicular to the axis 8 and advantageously constituted, in the example illustrated, by the stop plate 93 attached integrally to the shaft 7; this cam is more particularly visible in FIG. 4.
  • the cam 93 is pierced right through with a bore 94 allowing the passage of the tube 72 with a clearance comparable to that authorized by the bore 73; in the direction of a radial distance from the axis 8 and in any cutting plane perpendicular to this axis, it has an outer periphery 95 of ovoid shape.
  • a horizontal plane 96 including the axis 8 and fixed relative to the support 4 the shape of this periphery is indifferent provided that the cam 93 plays the role of abutment plate described above; below the plane 96, it has a circular shape with an axis 97 parallel to the axis 8 and located in the plane 14 under the axis 8, to define a cam path 98 having under the axis 8, in the plane 14, a point 99 which constitutes the point of the cam path 98 furthest from the axis 8, with a progressive decrease in the distance from the axis 8 for points of the cam path 98 more and more further from point 99, in a direction of travel of path 98 by rotation around axis 8, or in the opposite direction of travel.
  • the casing flange 19 presents opposite the cam path 98 two cam touches 101 and 102 each of which is integral with the flange 19 in rotation about the axis 8 but can slide relative to the housing flange 19, radially with reference to the axis 8, so as to be able to remain at contact of the cam track 98 whatever the angular position of the arm 29 relative to the support 4, around the axis 8, within normal operating limits.
  • the housing flange 19 is pierced, along respective axes 103 and 104 radial with respect to axis 8 and situated in the plane 100, of two bores 105 and 106 each of which opens into the housing 12, towards the cam path 98, being closed at the opposite by a respective plug 107,108; the axes 103 and 104 are arranged symmetrically to each other with respect to a plane which merges with the vertical plane 14 in the state of static equilibrium illustrated in FIGS.
  • this angular offset is at least equal to the angular movement of the arm 29 relative to the support 4, around the axis 8, under normal conditions of use; this offset is of the order of 70 ° in the example illustrated; naturally, this figure is given only by way of nonlimiting example.
  • each of the bores 105 and 106 is mounted, sliding along the axis 103, 104 of this bore, a respective piston 109, 110 that a respective compression compression helical spring 111, 112, interposed between this piston and the sealing plug the corresponding bore, resiliently biases towards the axis 8, so that each of the pistons 109, 110 protrudes from the corresponding bore 105, 106 inside the casing 22, and bears against the path of cam 98 by an end surface transverse to the axis of the corresponding bore, which surface defines the cam touch 101, 102.
  • This effect is used to produce a pumping of hydraulic fluid inside the casing 22 and to establish, by means of this hydraulic fluid, a pressure in the chamber 90 for biasing the braking piston 88.
  • each of the pistons 109 and 110 is hollow and present in the immediate vicinity of the corresponding cam touch 101, 102 a network of channels 131, 132 placed in such a way that these channels open out permanently inside the casing 22 whatever the point of the cam path 98 with which the contact of the cam touch 101, 102 within normal limits of use of the suspension member; inside the corresponding piston respectively, each of the networks of channels 131, 132 opens into an axial channel such as 113 provided with a non-return valve such as 114 of known structure, allowing a passage of fluid from the channels such as 131 towards the inside of the bore such as 105 via the channel such as 113, preventing passage in the opposite direction; thus, an exit movement of the piston results in the introduction, into the bore such as 105, of fluid coming from the casing 22 while a return movement of the piston in the bore causes a repression
  • the conduit 115 and its counterpart 116 corresponding to the bore 106 comprise a respective non-return valve 117, 118 of known type, allowing the passage of fluid in the direction of a discharge from the bore 105, 106 by prohibiting a passage in opposite direction, and the two conduits 115 and 116 meet, downstream of the non-return valves 117 and 118 with reference to the direction of passage authorized, in a single conduit 119 from which on the one hand derive a conduit 120 for connection to the chamber 90, and on the other hand two conduits 121 and 122 leading in parallel to a reservoir of hydraulic fluid 123 which can be constituted by the casing 22 itself.
  • the conduit 121 comprises in series an adjustable pressure relief valve 124, while the conduit 122 comprises an adjustable throttle 125 making it possible to establish through it an adjustable leakage rate; the constriction 125 can advantageously be controlled as a function of the pressures respectively downstream and upstream in the conduit 122 in order to eliminate the influence of the viscosity of the fluid, that is to say of the temperature, on this leakage rate .
  • one or other of the pistons 109, 110 causes a supply of the conduit 119 with hydraulic fluid. coming from the casing 22, with a flow rate which is a function of the speed of movement of the piston in its bore, that is to say of the speed of rotation of the arm relative to the support.
  • This flow passing through the constriction 125, produces a pressure which is a function of the pressure drop in said constriction and which is established uniformly in the conduits 119,120,121,122 and consequently in the chamber 90, which applies to the brake linings.
  • 84 and brake disc sectors 82 a mutual contact force directly dependent on the pressure prevailing in the conduit 119; from this mutual contact force results, by friction between the brake linings 84 and the brake disc sectors 82, a damping force having relative to the axis 8 a damping moment braking the rotation of the arm 29 in the direction considered, all the more so as the speed of this rotation is high; the loss of.
  • the damping force substantially proportional to the pressure prevailing in the chamber 90, itself a function of the pressure drop created at 125 by the flow of fluid in the conduit 122, tends to cancel out if this flow is canceled out, that is to say in particular when the arm 29 comes to a standstill relative to the support 4 between a rotation stroke in one direction and a rotation stroke in the other direction since the two pistons 109 and 110 are then immobile; to maintain a residual flow rate through the throttle 125 in the duct 122, that is to say prevent an almost total cancellation of the damping force, during the transient phases of reversal of the direction of rotation of the arm 29 around the axis 8 relative to the support 4, or preferably provides a pressure accumulator 130 connected to the conduit 119 by a conduit 129; this pressure accumulator 130 is calculated to have only a negligible effect on the pressure in the chamber 90 when the arm 29 rotates around the axis 8 relative to the support 4, while possibly only playing a role of filter reducing the effects of
  • the cam track 98 can be given an asymmetrical shape with respect to the plane 14 with which the plane of symmetry coincides between the respective axes 103, 104 of the bores 105, 106 when the arm 29 occupies its static equilibrium position and / or differentiate the respective sections of the pistons 109 and 110, so as to differentiate the damping force as a function of the direction of rotation of the arm 29 relative to the support 4.
  • these elements are permanently lubricated and cooled.
  • means may advantageously be provided to ensure that, despite the momentary withdrawals of the hydraulic fluid in the casing and the movement of the piston 47 in the jacket 44, and whatever the temperature to which this fluid is brought, the casing 22 is filled to the maximum with hydraulic fluid at least in certain angular positions of the arm relative to the support, under normal conditions of use.
  • a bladder 126 made of flexible, tight, elastically extensible material, which bladder contains a gas under pressure which, like the compressible fluid housed in the chambers 56 and 42, can advantageously be consisting of nitrogen; particularly advantageously, this bladder was placed in the chamber 41 delimited, inside the cavity 32, by the partition 40, so that due to such positioning, the variations in volume of the bladder 126 cause in the immediate vicinity of the brake linings 84 and sectors of the brake discs 82 a circulation of the hydraulic fluid of the housing 22.
  • the bladder 126 could be supplemented or replaced by accumulator means of the same function, arranged in an appropriate manner.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Vehicle Body Suspensions (AREA)

Claims (10)

1. Radaufhängung für ein Fahrzeug des Typs mit
- einem mit einem Gestell (2) des Fahrzeugs fest verbindbaren Träger (4),
- einem Längslenker (29),
- Mitteln (36) zum Verbinden eines Lauforgans (3) mit dem Lenker (29), die eine erste quergerichtete Achse (37) bilden, um die sich das Lauforgan (3) gegenüber dem Lenker (29) dreht,
- Mitteln (7, 9, 16, 17, 18) zum Verbinden des Lenkers (29) mit dem Träger (4), die eine zweite quergerichtete Achse (8) bilden, um die sich der Lenker (29) gegenüber dem Träger (4) dreht, wobei die zweite Achse (8) zur ersten Achse (37) parallel und ihr gegenüber in Längsrichtung versetzt angeordnet ist,
- einem im Lenker (29) ausgebildeten Längszylinder (44),
- einem im Zylinder (44) längsverschiebbar angeordneten Kolben (47), der mit dem Zylinder (44) eine dichte Umschließung (42, 56) begrenzt,
- einem eine Feder bildenden kompressiblen Fluid in der Umschließung (42, 56),
- einer Koppelstange zur Verbindung des Kolbens (47) mit dem Träger (4),
- Mitteln (12, 51) zur gelenkigen Verbindung der Koppelstange (49) mit dem Träger (4) um eine dritte quergerichtete Achse (13), die zur zweiten Achse (8) parallel und ihr gegenüber in Querrichtung versetzt angeordnet ist,
- Mitteln (52, 54, 55, 60) zum Verbinden der Koppelstange (49) mit dem Kolben (47) um eine zur dritten Achse (13) parallele vierte quergerichtete Achse (53),
dadurch gekennzeichnet, daß die Mittel (52, 54, 55, 60) zum Verbinden der Koppelstange (49) mit dem Kolben (47) umfassen:
- einen im Zylinder (44) längsverschiebbar und in Längsrichtung auf der der Koppelstange (49) zugewandten Seite neben dem Kolben (47) angeordneten Schieber (55),
- Mittel (52, 54) zum gelenkigen Verbinden der Koppelstange (49) mit dem Schieber (55) um die vierte Achse (53),
- Mittel (52, 60) zum Verbinden des Schiebers (55) mit dem Kolben (47), welche die gegenseitige Übertragung von Längskräften ohne gegenseitige Übertragungen von Querkräften ermöglichen.
2. Radaufhängung für ein Fahrzeug nach Anspruch 1, dadurch gekennzeichnet, daß die Mittel (52, 60) zum Verbinden des Schiebers (55) mit dem Kolben (47) aus gegenseitige Anschläge in der Richtung relativer Annäherung in Längsrichtung bildenden Mitteln (52, 60) bestehen.
3. Radaufhängung für ein Fahrzeug nach Anspruch 2, dadurch gekennzeichnet, daß die Mittel (52, 54) zum gelenkigen Verbinden der Koppelstange (49) mit dem Schieber (55) einen Koppelstangenkopf (52) umfassen, der zum Kolben (47) hin von Rotationsgestalt um die vierte Achse (53) ist, und daß der Koppelstangenkopf (52) ein Länganschlagglied des Schiebers (55) gegenüber dem Kolben (47) bildet.
4. Radaufhängung für ein Fahrzeug nach einem der Ansprüche 2 und 3, dadurch gekennzeichnet, daß der Kolben (47) zum Schieber (55) hin einen mit ihm fest verbundenen eingesetzten Puffer (60) trägt, der ein Anschlagglied des Kolbens (47) gegenüber dem Schieber (55) bildet.
5. Radaufhängung für ein Fahrzeug nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Mittel (52, 54) zum gelenkigen Verbinden der Koppelstange (49) mit dem Schieber (55) um die vierte Achse (53) aus Kugelgelenkgliedern (52, 54) bestehen.
6. Radaufhängung für ein Fahrzeug nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Mittel (12, 51) zum gelenkigen Verbinden der Koppelstange (49) mit dem Träger (4) um die dritte Achse (13) aus Kugelgelenkgliedern (12, 51) bestehen.
7. Radaufhängung für ein Fahrzeug nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß sie Mittel (22, 59) zum Einleiten eines Schmiermittels zwischen den Schieber und den Kolben (47) aufweist.
8. Radaufhängung für ein Fahrzeug nach Anspruch 7, dadurch gekennzeichnet, daß die Mittel (22, 59) zum Einleiten eines Schmiermittels zwischen den Schieber (55) und den Kolben (47) Mittel (22) zur Bildung einer Schmiermittelreserve auf der dem Kolben (47) abgewandten Seite des Schiebers (55) und Mittel (59) zum Durchlassen von Fluid zwischen der dem Kolben (47) zugewandten und der entgegengesetzten Seite des Schiebers (55) umfassen.
9. Radaufhängung für ein Fahrzeug nach Anspruch 8, dadurch gekennzeichnet, daß die Mittel (59) zum Durchlassen von Fluid Kanäle (59) umfassen, die den Schieber (55) in Längsrichtung vom einen zum anderen Ende durchsetzen.
10. Radaufhängung für ein Fahrzeug nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß der Zylinder (44) von einer in den Lenker (29) eingesetzten längsgerichteten Büchse (44) gebildet ist.
EP86402036A 1985-09-19 1986-09-17 Federungsaggregat mit Schwingenarm für Fahrzeuge Expired - Lifetime EP0220094B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8513934 1985-09-19
FR8513934A FR2587278B1 (fr) 1985-09-19 1985-09-19 Organe de suspension a bras oscillant, pour vehicules

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EP0220094A1 EP0220094A1 (de) 1987-04-29
EP0220094B1 true EP0220094B1 (de) 1990-03-07

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EP86402036A Expired - Lifetime EP0220094B1 (de) 1985-09-19 1986-09-17 Federungsaggregat mit Schwingenarm für Fahrzeuge

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US (1) US4721328A (de)
EP (1) EP0220094B1 (de)
BR (1) BR8604480A (de)
DE (1) DE3669292D1 (de)
ES (1) ES2002356A6 (de)
FR (1) FR2587278B1 (de)

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FR2686563B1 (fr) * 1992-01-27 1994-03-18 Messier Bugatti Ensemble de suspension pour vehicule lourd, notamment pour vehicule chenille.
DE19635681A1 (de) * 1996-09-03 1998-03-05 Marker Deutschland Gmbh Schuhhalteraggregat
US20040163869A1 (en) * 2003-02-21 2004-08-26 Chun Wendell H. Articulated vehicle suspension system shoulder joint
US20050023052A1 (en) * 2003-02-21 2005-02-03 Beck Michael S. Vehicle having an articulated suspension and method of using same
US7150340B2 (en) * 2003-02-21 2006-12-19 Lockheed Martin Corporation Hub drive and method of using same
US8839891B2 (en) 2003-02-21 2014-09-23 Lockheed Martin Corporation Multi-mode skid steering
US7464775B2 (en) * 2003-02-21 2008-12-16 Lockheed Martin Corporation Payload module for mobility assist
US20040232632A1 (en) * 2003-02-21 2004-11-25 Beck Michael S. System and method for dynamically controlling the stability of an articulated vehicle
US7273117B2 (en) * 2003-05-15 2007-09-25 General Dynamics Land Systems, Inc. Vehicle suspension apparatus
US20050205329A1 (en) * 2004-02-25 2005-09-22 Shimon Fanger-Vexler Vehicle and vehicle drive-through suspension arm
WO2008048199A2 (en) * 2005-03-04 2008-04-24 Board Of Regents, The University Of Texas System Suspension-related systems and methods
DE202005008838U1 (de) * 2005-06-03 2005-08-18 Kendrion Rsl Gmbh & Co. Kg Vorrichtung zur Verlangsamung der relativen Drehbewegung von zueinander beweglich angeordneten Bauteilen
GB2480630A (en) * 2010-05-25 2011-11-30 Horstman Defence Systems Ltd A suspension unit for use on a tracked vehicle
GB2482855A (en) * 2010-05-25 2012-02-22 Horstman Defence Systems Ltd A suspension unit for use on a tracked vehicle

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DE2525493A1 (de) * 1975-06-07 1976-12-09 Thyssen Industrie Hydropneumatisches federelement
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Publication number Publication date
EP0220094A1 (de) 1987-04-29
FR2587278A1 (fr) 1987-03-20
US4721328A (en) 1988-01-26
DE3669292D1 (de) 1990-04-12
FR2587278B1 (fr) 1987-12-24
BR8604480A (pt) 1987-05-19
ES2002356A6 (es) 1988-08-01

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